U.S. patent number 7,726,141 [Application Number 10/871,703] was granted by the patent office on 2010-06-01 for refrigerator, and method for controlling operation of the same.
This patent grant is currently assigned to LG Electronics Inc.. Invention is credited to Bong-Jun Choi, Samchul Ha, Jun-Hyeon Hwang, Yunho Hwang, Young Jeong, Young-Hwan Ko, Jongmin Shin, Jae-Seng Sim.
United States Patent |
7,726,141 |
Sim , et al. |
June 1, 2010 |
**Please see images for:
( Certificate of Correction ) ** |
Refrigerator, and method for controlling operation of the same
Abstract
A refrigerator is provided which can individually cool a
freezing chamber and a refrigerating chamber by dividing a heat
exchange region of an evaporator into a freezing chamber side
region and a refrigerating chamber side region, forming individual
circulation passages for supplying cool air from each region to the
freezing chamber and the refrigerating chamber, and forming a
freezing chamber fan and a refrigerating chamber fan on each
circulation passage. Further, a method for controlling operation of
the same is provided which can efficiently perform a cooling
operation and reduce power consumption by effectively controlling
the operations of each component.
Inventors: |
Sim; Jae-Seng (Masan-Shi,
KR), Ko; Young-Hwan (Changwon-Shi, KR),
Shin; Jongmin (Busan, KR), Choi; Bong-Jun
(Changwon-shi, KR), Hwang; Jun-Hyeon (Changwon-Shi,
KR), Jeong; Young (Gwangmeong-Shi, KR), Ha;
Samchul (Changwon-Shi, KR), Hwang; Yunho
(Ellicott City, MD) |
Assignee: |
LG Electronics Inc. (Seoul,
KR)
|
Family
ID: |
35479164 |
Appl.
No.: |
10/871,703 |
Filed: |
June 21, 2004 |
Prior Publication Data
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Document
Identifier |
Publication Date |
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US 20050279119 A1 |
Dec 22, 2005 |
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US 20080229777 A9 |
Sep 25, 2008 |
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Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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10537828 |
Jun 8, 2005 |
7584627 |
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Current U.S.
Class: |
62/179; 62/441;
62/419; 62/234 |
Current CPC
Class: |
F25D
21/08 (20130101); F25B 39/022 (20130101); F25D
11/02 (20130101); F25D 29/00 (20130101); F25D
17/065 (20130101); F25D 2400/06 (20130101); F25D
2700/12 (20130101); Y10T 137/7737 (20150401); F25D
2317/0683 (20130101); F25D 2700/122 (20130101); F25B
2600/2511 (20130101); F25B 2400/052 (20130101); F25B
41/385 (20210101); F25B 41/39 (20210101); F25B
2500/01 (20130101) |
Current International
Class: |
F25D
17/00 (20060101) |
Field of
Search: |
;62/179,180,441,443,81,151,276,155,234,419,314,414,446,450 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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0 984 229 |
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Mar 2000 |
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EP |
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0 791 162 |
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Mar 2004 |
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EP |
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1 596 143 |
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Nov 2005 |
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EP |
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09-229532 |
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Sep 1997 |
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JP |
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11-173729 |
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Jul 1999 |
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JP |
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2001-4260 |
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Jan 2001 |
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JP |
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10-0189103 |
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Jan 1999 |
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KR |
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10-2001-0026227 |
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Apr 2001 |
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KR |
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10-2003-0027368 |
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Apr 2003 |
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KR |
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WO 00/79192 |
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Dec 2000 |
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WO |
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Other References
Abstract of JP 09-229532 to Asakawa et al. cited by examiner .
Search Report. cited by other .
European Office Action dated Jan. 14, 2008. cited by other.
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Primary Examiner: Ali; Mohammad M
Attorney, Agent or Firm: KED & Associates, LLP
Parent Case Text
This application is a Continuation-In-Part of U.S. patent
application Ser. No. 10/537,828, filed Jun. 8, 2005, now U.S. Pat.
No. 7,584,627 which claims priority to PCT/KR03/02749, filed Dec.
16, 2003, which claims priority to Korean Patent Application
10-2002-0083289 filed Dec. 24, 2002 in Korea.
Claims
What is claimed is:
1. A refrigerator, comprising: a compressor being operated to
compress refrigerants into high temperature high pressure gas
refrigerants; a condenser being operated to condense the
refrigerants compressed in the compressor into high temperature
high pressure liquid refrigerants; a decompression device being
operated to expand the refrigerants condensed in the condenser into
low temperature low pressure liquid refrigerants; an evaporator
being operated to evaporate the refrigerants expanded in the
decompression device into low temperature low pressure gas
refrigerants, wherein a heat exchange region of the evaporator is
divided into a freezing chamber side region and a refrigerating
chamber side region by a blocking plate; a freezing chamber
circulation passage formed in the refrigerator and being operated
to supply cool air from the freezing chamber side region into a
freezing chamber, wherein a freezing chamber fan is installed in
the freezing chamber circulation passage and is being operated to
direct cool air to the freezing chamber; a refrigerating chamber
circulation passage formed in the refrigerator that is separate
from the freezing chamber circulation passage, wherein the
refrigerating chamber circulation passage is being operated to
supply cool air from the refrigerating chamber side region into a
refrigerating chamber, wherein a refrigerating chamber fan is
installed in the refrigerating chamber circulation passage and is
being operated to direct cool air to the refrigerating chamber,
wherein the decompression device comprises a freezing expansion
means and a refrigerating expansion means installed side by side
between the condenser and the evaporator to combine refrigerant
tubes formed at the front and rear ends, the freezing expansion
means and the refrigerating expansion means being different in
capacity; and a valve device installed between the condenser and
the freezing expansion means and the refrigerating expansion means,
wherein the valve device is being operated to selectively supply
the refrigerants from the condenser to the freezing expansion valve
or the refrigerating expansion valve, and wherein, in a freezing
and refrigerating mode for making a temperature of the freezing
chamber and a temperature of the refrigerating chamber reach a set
freezing temperature and a set refrigerating temperature,
respectively, the valve device directs the refrigerants to pass
through the freezing expansion means, the freezing chamber fan is
continuously operated, and the refrigerating chamber fan is
operated and stopped at intervals of a predetermined period of
time.
2. The refrigerator of claim 1, wherein the freezing expansion
means and the refrigerating expansion valve are capillary
tubes.
3. The refrigerator of claim 1, wherein the valve device is a three
way valve installed on a refrigerant tube branched from the
condenser into the freezing expansion means and the refrigerating
expansion valve, being operated to vary a passage of the
refrigerants.
4. The refrigerator of claim 3, wherein the valve device comprises
first and second solenoid valves installed on refrigerant tubes
formed at the front ends of the freezing expansion valve and the
refrigerating expansion means, being operated to vary a passage of
the refrigerants.
5. The refrigerator of claim 1, wherein, in the freezing mode for
making the temperature of the freezing chamber reach a set freezing
temperature, the valve device directs the refrigerants to pass
through the freezing expansion means, the freezing chamber fan is
operated, and the refrigerating chamber fan is stopped.
6. The refrigerator of claim 1, wherein, in the refrigerating mode
for making the temperature of the refrigerating chamber reach a set
refrigerating temperature, the valve device directs the
refrigerants to pass through the refrigerating expansion means, the
refrigerating chamber fan is operated, and the freezing chamber fan
is stopped.
7. A refrigerator, comprising: a compressor being operated to
compress refrigerants into high temperature high pressure gas
refrigerants; a condenser being operated to condense the
refrigerants compressed in the compressor into high temperature
high pressure liquid refrigerants; a decompression device being
operated to expand the refrigerants condensed in the condenser into
low temperature low pressure liquid refrigerants; an evaporator
being operated to evaporate the refrigerants expanded in the
decompression device into low temperature low pressure gas
refrigerants, wherein a heat exchange region of the evaporator is
divided into a freezing chamber side region and a refrigerating
chamber side region by a blocking plate; a freezing chamber
circulation passage formed in the refrigerator and being operated
to supply cool air from the freezing chamber side region into a
freezing chamber, wherein a freezing chamber fan is installed in
the freezing chamber circulation passage and is being operated to
direct cool air to the freezing chamber; a refrigerating chamber
circulation passage formed in the refrigerator that is separate
from the freezing chamber circulation passage, wherein the
refrigerating chamber circulation passage is being operated to
supply cool air from the refrigerating chamber side region into a
refrigerating chamber, wherein a refrigerating chamber fan is
installed in the refrigerating chamber circulation passage and is
being operated to direct cool air to the refrigerating chamber,
wherein the decompression device comprises a freezing expansion
means and a refrigerating expansion means installed side by side
between the condenser and the evaporator to combine refrigerant
tubes formed at the front and rear ends, the freezing expansion
means and the refrigerating expansion means being different in
capacity; and a valve device installed between the condenser and
the freezing expansion means and the refrigerating expansion means,
wherein the valve device is being operated to selectively supply
the refrigerants from the condenser to the freezing expansion valve
or the refrigerating expansion valve, and wherein, in a defrosting
mode for making a temperature of the freezing chamber and a
temperature of the refrigerating chamber reach a defrosting
temperature for removing ice from a surface of the evaporator, the
compressor is stopped, the valve device prevents the refrigerants
from passing through the freezing expansion means or the
refrigerating expansion means, the freezing chamber fan is stopped,
and the refrigerating chamber fan is operated.
8. The refrigerator of claim 7, wherein, in the defrosting mode,
when the temperature of the freezing chamber and the temperature of
the refrigerating chamber do not reach the defrosting temperature,
the valve device directs the refrigerants to pass through the
freezing expansion means and the refrigerating expansion means, and
defrosting heaters installed at a lower portion of the evaporator
are heated.
9. The refrigerator of claim 7, wherein the freezing expansion
means and the refrigerating expansion means are capillary
tubes.
10. The refrigerator of claim 7, wherein the valve device is a
three way valve installed on a refrigerant tube branched from the
condenser into the freezing expansion means and the refrigerating
expansion means, being operated to vary a passage of the
refrigerants.
11. The refrigerator of claim 10, wherein the valve device
comprises first and second solenoid valves installed on refrigerant
tubes formed at the front ends of the freezing expansion means and
the refrigerating expansion means, being operated to vary a passage
of the refrigerants.
12. The refrigerator of claim 7, wherein, in the freezing mode for
making the temperature of the freezing chamber reach a set freezing
temperature, the valve device directs the refrigerants to pass
through the freezing expansion means, the freezing chamber fan is
operated, and the refrigerating chamber fan is stopped.
13. The refrigerator of claim 7, wherein, in the refrigerating mode
for making the temperature of the refrigerating chamber reach a set
refrigerating temperature, the valve device directs the
refrigerants to pass through the refrigerating expansion means, the
refrigerating chamber fan is operated, and the freezing chamber fan
is stopped.
14. The refrigerator of claim 8, wherein the defrosting heaters
comprises a defrosting heater for the freezing chamber having a
relatively large capacity installed at the lower portion of the
freezing chamber side region of the evaporator and a defrosting
heater for the refrigerating chamber having a relatively small
capacity installed at the lower portion of the refrigerating
chamber side region of the evaporator.
15. The refrigerator of claim 14, wherein the defrosting heaters
comprises radiant heaters.
Description
TECHNICAL FIELD
The present invention relates to a refrigerator which can
efficiently perform a cooling operation and reduce power
consumption, by individually cooling a freezing chamber and a
refrigerating chamber and effectively controlling the operations of
each component, and a method for controlling an operation of the
same.
BACKGROUND ART
In general, a refrigerator is one of the living necessaries which
preserves food fresh for a predetermined period, by lowering a
temperature of a freezing chamber or a refrigerating chamber by
repeating a refrigeration cycle of compressing, condensing,
expanding and evaporating refrigerants.
The refrigerator has a refrigeration cycle including basic
components such as a compressor for compressing refrigerants into
high temperature high pressure gas refrigerants, a condenser for
condensing the refrigerants from the compressor into high
temperature high pressure liquid refrigerants, an expansion valve
for decompressing the refrigerants from the condenser into low
temperature low pressure liquid refrigerants, and an evaporator for
maintaining a low temperature in a freezing chamber or a
refrigerating chamber, by absorbing heat from the freezing chamber
or the refrigerating chamber by evaporating the refrigerants from
the expansion valve into low temperature low pressure gas
refrigerants.
FIG. 1 is a schematic front perspective view illustrating a
conventional side-by-side type refrigerator, and FIG. 2 is a
structure view illustrating a refrigeration cycle applied to the
refrigerator of FIG. 1.
The conventional side-by-side type refrigerator in which a freezing
chamber and a refrigerating chamber are disposed side by side will
now be described with reference to FIGS. 1 and 2. A refrigeration
cycle including a compressor 12, a condenser 14, an expansion valve
16 and an evaporator 18 is built in an inner wall, for generating
cool air by the evaporator 18. The freezing chamber F maintaining
about -18.degree. C. by sucking most of the cool air, and the
refrigerating chamber R maintaining about 0 to 7.degree. C. by
sucking part of the cool air are disposed side by side at both
sides of a main body 2.
The refrigeration cycle includes basic components, and thus
explanations thereof are omitted.
Here, the freezing chamber F and the refrigerating chamber R are
divided by a cross wall 4. Part of the cross wall 4 is opened so
that the cool air can flow between the freezing chamber F and the
refrigerating chamber R.
The evaporator 18 is installed on the inner wall in the freezing
chamber F, and a blast fan 22 is installed at the upper portion of
the evaporator 18, for sending cool air generated in the evaporator
18 to the freezing chamber F or the refrigerating chamber R.
Generally, an axial flow fan for sucking and discharging cool air
in an axial direction is used.
The freezing chamber F and the refrigerating chamber R compose a
cool air circulation structure for circulating cool air near the
evaporator 18 through the freezing chamber F and the refrigerating
chamber R by the operation of the blast fan 22, and returning the
cool air to the evaporator 18.
The operations of the components of the refrigerator are controlled
by a microcomputer (not shown). The microcomputer controls the
whole components so that a temperature Tf of the freezing chamber F
and a temperature Tr of the refrigerating chamber R can reach a set
freezing temperature Tf.sub.0 and a set refrigerating temperature
Tr.sub.0 setting by the user or automatically set.
In the conventional refrigerator, when a load is applied, the
compressor 12 is operated according to a control signal from the
microcomputer, and refrigerants are circulated though the
compressor 12, the condenser 14, the expansion valve 16 and the
evaporator 18, for cooling air near the evaporator 18 and
generating cool air.
In addition, the blast fan 22 is operated according to a control
signal from the microcomputer, so that most of the cool air near
the evaporator 18 can be supplied to the freezing chamber F and
part of the cool air can be supplied to the refrigerating chamber
R. The cool air circulated in the freezing chamber F and the
refrigerating chamber R to have a high temperature is resupplied to
the evaporator 18.
In the conventional refrigerator, one evaporator 18 is installed in
the freezing chamber F, and the cool air heat-exchanged through the
evaporator 18 is partially distributed and supplied to the
refrigerating chamber R on the passage of the freezing chamber F.
Accordingly, when the inside temperature of any one of the freezing
chamber F and the refrigerating chamber R does not satisfy the set
freezing temperature Tf.sub.0 or the set refrigerating temperature
Tr.sub.0, the compressor 12 and the blast fan 22 are operated to
lower the temperature, thereby increasing power consumption or
supercooling food.
For example, when the temperature Tf of the freezing chamber F
reaches the set freezing temperature Tf.sub.0, if the temperature
Tr of the refrigerating chamber R does not satisfy the set
refrigerating temperature Tr.sub.0, the temperature Tr of the
refrigerating chamber R must be lowered to reach the set
refrigerating temperature Tr.sub.0 by operating the compressor 12
and the blast fan 22. Here, the cool air is also supplied to the
freezing chamber F, to unnecessarily lower the temperature Tf of
the freezing chamber F. In addition, power consumption
increases.
On the other hand, when the temperature Tr of the refrigerating
chamber R reaches the set refrigerating temperature Tr.sub.0, if
the temperature Tf of the freezing chamber F does not satisfy the
set freezing temperature Tf.sub.0, the temperature Tf of the
freezing chamber F must be lowered to reach the set freezing
temperature Tf.sub.0 by operating the compressor 12 and the blast
fan 22. The cool air is also supplied to the refrigerating chamber
R, to unnecessarily lower the temperature Tr of refrigerating
chamber R. Moreover, food is supercooled.
In the conventional refrigerator, part of the cool air from the
evaporator 18 is distributed to the refrigerating chamber R. A
volume of the cool air distributed to the refrigerating chamber R
is relatively smaller than a volume of the cool air distributed to
the freezing chamber F. Therefore, a cooling speed of the
refrigerating chamber R is reduced, to unnecessarily operate the
compressor 12.
For example, when the temperature Tr of the refrigerating chamber R
does not reach the set refrigerating temperature Tr.sub.0, the
compressor 12 is operated until the temperature Tr of the
refrigerating chamber R reaches the set refrigerating temperature
Tr.sub.0. Accordingly, an excessive load is applied to the
compressor 12 to reduce the temperature of the evaporator 18 lower
than the temperature Tf of the freezing chamber F.
DISCLOSURE OF THE INVENTION
The present invention is achieved to solve the above problems. An
object of the present invention is to provide a refrigerator which
can improve cooling efficiency and reduce power consumption, by
individually cooling a freezing chamber and a refrigerating
chamber, and a method for controlling an operation of the same.
Another object of the present invention is to provide a
refrigerator which can prevent a compressor from being
unnecessarily operated, by increasing a cooling speed of a
refrigerating chamber as well as a cooling speed of a freezing
chamber so that a temperature of the refrigerating chamber can
rapidly reach a set refrigerating temperature, and a method for
controlling an operation of the same.
Yet another object of the present invention is to provide a
refrigerator which can increase an inside capacity of a freezing
chamber or a refrigerating chamber, and a method for controlling an
operation of the same.
Yet another object of the present invention is to provide a
refrigerator which can prevent an evaporator from being frosted and
effectively perform a defrosting operation, and a method for
controlling an operation of the same.
In order to achieve the above-described objects of the present
invention, there is provided a refrigerator including: a compressor
for compressing refrigerants into high temperature high pressure
gas refrigerants; a condenser for condensing the refrigerants
compressed in the compressor into high temperature high pressure
liquid refrigerants; a decompression means for expanding the
refrigerants condensed in the condenser into low temperature low
pressure liquid refrigerants; an evaporator for evaporating the
refrigerants expanded in the decompression means into low
temperature low pressure gas refrigerants, a heat exchange region
of which being divided into a freezing chamber side region and a
refrigerating chamber side region; and an air blast device linked
respectively to the freezing chamber side region and the
refrigerating chamber side region of the evaporator, for sending
cool air from each region to a freezing chamber and a refrigerating
chamber.
According to another aspect of the present invention, a method for
controlling an operation of a refrigerator includes: a first step
for compressing refrigerants into high temperature high pressure
gas refrigerants according to a freezing load or a refrigerating
load applied to a freezing chamber or a refrigerating chamber, a
second step for condensing the refrigerants compressed in the first
step into high temperature high pressure liquid refrigerants by
performing a heat exchange operation with air; a third step for
decompressing the refrigerants condensed in the second step into
low temperature low pressure liquid refrigerants by controlling a
decompression degree according to the load; and a fourth step for
generating cool air by evaporating the refrigerants decompressed in
the third step into low temperature low pressure gas refrigerants
by performing a heat exchange operation with air, and selectively
sending the cool air to the freezing chamber, the refrigerating
chamber, or both the freezing chamber and the refrigerating chamber
according to the load.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention will become better understood with reference
to the accompanying drawings which are given only by way of
illustration and thus are not limitative of the present invention,
wherein:
FIG. 1 is a schematic front perspective view illustrating a
conventional side-by-side type refrigerator;
FIG. 2 is a structure view illustrating a refrigeration cycle
applied to the refrigerator of FIG. 1;
FIG. 3 is a front perspective view illustrating a side-by-side type
refrigerator in accordance with a first embodiment of the present
invention;
FIG. 4 is a cross-sectional view illustrating the refrigerator of
FIG. 3;
FIG. 5 is a front perspective view illustrating a side-by-side type
refrigerator in accordance with a second embodiment of the present
invention;
FIG. 6 is a cross-sectional view illustrating the refrigerator of
FIG. 5:
FIG. 7 is a structure view illustrating a first example of a
refrigeration cycle applied to the refrigerators of FIGS. 3 and
5;
FIG. 8 is a structure view illustrating a second example of the
refrigeration cycle applied to the refrigerators of FIGS. 3 and
5;
FIG. 9 is a structure view illustrating a third example of the
refrigeration cycle applied to the refrigerators of FIGS. 3 and
5;
FIG. 10 is a perspective view illustrating a first example of an
evaporator applied to the refrigerators of FIGS. 3 and 5;
FIG. 11 is a perspective view illustrating a second example of the
evaporator applied to the refrigerators of FIGS. 3 and 5; and
FIG. 12 is a flowchart showing sequential steps of a method for
controlling an operation of a refrigerator in accordance with a
preferred embodiment of the present invention.
BEST MODE FOR CARRYING OUT THE INVENTION
A refrigerator and a method for controlling an operation of the
same in accordance with the present invention will now be described
in detail with reference to the accompanying drawings.
FIG. 3 is a front perspective view illustrating a side-by-side type
refrigerator in accordance with a first embodiment of the present
invention, and FIG. 4 is a cross-sectional view illustrating the
refrigerator of FIG. 3.
The refrigerator in accordance with the first embodiment of the
present invention will now be described with reference to FIGS. 3
and 4. A freezing chamber F and a refrigerating chamber R are
disposed side by side at both sides of a main body 52 from a cross
wall 54. A compressor (not shown), a condenser (not shown) and an
expansion means (not shown) are built in a machine room (not shown)
formed at one side of the freezing chamber F and the refrigerating
chamber R. An evaporator 68 is built in the freezing chamber F, for
generating cool air by performing a heat exchange operation with
refrigerants.
Especially, the evaporator 68 is divided into a freezing chamber
side region 68a and a refrigerating chamber side region 68b.
Individual circulation passages are formed to circulate the cool
air heat-exchanged in each region in the freezing chamber F and the
refrigerating chamber R, respectively. A freezing chamber fan 72
and a refrigerating chamber fan 74 for sending the cool air from
the freezing chamber side region 68a and the refrigerating chamber
side region 68b to the freezing chamber F and the refrigerating
chamber R, respectively, and motors (not shown) for driving the
fans 72 and 74 are installed on the circulation passages to be
linked to the freezing chamber side region 68a and the
refrigerating chamber side region 68b.
Preferably, the compressor is a capacity variable compressor such
as an inverter compressor or a linear compressor to control a
compression flow rate, and the expansion means is a capillary tube
having a relatively small refrigerant tube diameter or an
electronic expansion valve controlling opening.
In the evaporator 68, a heat exchange region is divided by a
special blocking plate 70 so that the freezing chamber side region
68a and the refrigerating chamber side region 68b can be disposed
side by side.
Here, the evaporator 68 is a straight type thin heat exchanger in
which a plurality of cooling fins 68B are installed vertically to a
refrigerant tube 68A. The blocking plate 70 is installed between
the cooling fins 68B. As shown in FIGS. 10 and 11, plurality of
grooves 70a are formed on the surface of the blocking plate 70, for
forming a turbulent bed to the cool air flowing along the surface
of the evaporator 68, thereby improving heat exchange
efficiency.
As shown in FIG. 11, in the evaporator 68, the freezing chamber
side region 68a and the refrigerating chamber side region 68b an
have the same area. Generally, in order to maintain the freezing
chamber F at a lower temperature than the refrigerating chamber R,
lower temperature cool air is necessary in the freezing chamber F.
Accordingly, as depicted in FIG. 10, the freezing chamber side
region 68a is preferably larger than the refrigerating chamber side
region 68b.
In addition, in the evaporator 68, the freezing chamber side region
68a maintains a lower temperature than the refrigerating chamber
side region 68b, and thus is more easily frosted than the
refrigerating chamber side region 68b. Therefore, a cooling fin
pitch a of the freezing chamber side region 68a is set wider than a
cooling fin pitch b of the refrigerating chamber side region 68b,
to efficiently prevent frost.
The refrigerating chamber side region 68b is narrower than the
freezing chamber side region 68a, to reduce heat exchange
efficiency. Here, the cooling fan pitch b of the refrigerating
chamber side region 68b is narrower than the cooling fan pitch a of
the freezing chamber side region 68a. Accordingly, more cooling
fins are installed in a unit area of the refrigerating chamber side
region 68b, thereby improving heat exchange efficiency in the
refrigerating chamber side region 68b.
Preferably, at least one defrosting heater (not shown) is installed
at the lower portion of the evaporator 68, for performing a
defrosting operation. A defrosting heater (not shown) for the
freezing chamber F is installed at the lower portion of the
freezing chamber side region 68a, for defrosting the freezing
chamber side region 68a, and a defrosting heater (not shown) for
the refrigerating chamber R is installed at the lower portion of
the refrigerating chamber side region 68b, for defrosting the
refrigerating chamber side region 68b.
Preferably, the defrosting heater for the freezing chamber F and
the defrosting heater for the refrigerating chamber R are radiant
heaters for transmitting heat to the evaporator 68 by radiation.
The defrosting heater for the freezing chamber F has a larger
capacity than the defrosting heater for the refrigerating chamber
R, thereby rapidly defrosting the freezing chamber side region
68a.
The freezing chamber fan 72 and the refrigerating chamber fan 74
are disposed side by side at the upper portions of the freezing
chamber side region 68a and the refrigerating chamber side region
68b, for sending the refrigerants from the evaporator 68 to the
freezing chamber F and the refrigerating chamber R, respectively.
Recently, as a large volume of cool air is required due to increase
of a capacity of the refrigerator, sirocco fans which are
centrifugal fans which have a relatively large air blast volume and
which can be effectively installed in a restricted space of the
upper portion of the evaporator 68 which is a thin heat exchanger
are used as the freezing chamber fan 72 and the refrigerating
chamber fan 74.
That is, the freezing chamber fan 72 and the refrigerating chamber
fan 74 are sirocco fans for sucking air in an axial direction and
discharging air in a radius direction. Therefore, the freezing
chamber fan 72 and the refrigerating chamber fan 74 are disposed
side by side at the upper portion of the evaporator 68 in an axial
direction and installed on the individual circulation passages,
respectively, so that the cool air from the evaporator 68 can be
supplied to both sides of the freezing chamber fan 72 and the
refrigerating chamber fan 74 and discharged to the front surface
thereof.
Preferably, the motors for driving the freezing chamber fan 72 and
the refrigerating chamber fan 74 are BLDC motors. Because the BLDC
motor uses a driving circuit for converting an alternating current
to a direct current instead of using a brush, the BLDC motor does
not generate a spark by a carbon material brush, prevents gas
explosion, is stably driven in most of rotation numbers, and
maintains high efficiency of 70 to 80%.
In accordance with the first embodiment of the present invention,
there are formed the circulation passage for the freezing chamber F
for discharging the cool air from the freezing chamber side region
68a of the evaporator 68 to the freezing chamber F, circulating the
cool air in the freezing chamber F, and re-supplying the circulated
air to the freezing chamber side region 68a of the evaporator 68,
and the circulation passage for the refrigerating chamber R for
discharging the cool air from the refrigerating chamber side region
68b of the evaporator 68 to the refrigerating chamber R,
circulating the cool air in the refrigerating chamber R, and
re-supplying the circulated air to the refrigerating chamber side
region 68b.
Here, the evaporator 68 is installed on the inner wall of the
freezing chamber F. Accordingly, the circulation passage for the
refrigerating chamber R including a suction passage for the
refrigerating chamber R and a discharge passage for the
refrigerating chamber R is formed between the refrigerating chamber
side region 68b and the refrigerating chamber R, and the
circulation passage for the freezing chamber F is automatically
formed in the other regions.
The cool air is individually circulated in the freezing chamber F
and the refrigerating chamber R to efficiently cool the freezing
chamber F and the refrigerating chamber R. Even if a door of the
freezing chamber F or the refrigerating chamber R is opened/closed,
the other door is not moved.
On the other hand, a connection passage 54c is formed on the cross
wall 54 between the freezing chamber F and the refrigerating
chamber R, so that the cool air can flow therethrough. A damper 54d
is installed to be opened/closed on the connection passage. The
damper 54d is opened/closed by the microcomputer for controlling
the operation of the refrigerator, for supplying part of the cool
air of the freezing chamber F to the refrigerating chamber R.
FIG. 5 is a front perspective view illustrating a side-by-side type
refrigerator in accordance with a second embodiment of the present
invention, and FIG. 6 is a cross-sectional view illustrating the
refrigerator of FIG. 5.
The refrigerator in accordance with the second embodiment of the
present invention will now be explained with reference to FIGS. 5
and 6. Identically to the first embodiment, a freezing chamber F
and a refrigerating chamber R are disposed side by side at both
sides of a main body 52 from a cross wall 54. A compressor (not
shown), a condenser (not shown) and an expansion means (not shown)
are built in a machine room (not shown) formed at one side of the
freezing chamber F and the refrigerating chamber R. An evaporator
68 is built in the freezing chamber F and the refrigerating chamber
R for generating cool air by performing a heat exchange operation
with refrigerants.
Especially, the evaporator 68 is divided into a freezing chamber
side region 68a and a refrigerating chamber side region 68b by the
cross wall 54. Individual circulation passages are formed to
circulate the cool air heat-exchanged in each region in the
freezing chamber F and the refrigerating chamber R, respectively. A
freezing chamber fan 72 and a refrigerating chamber fan 74 for
sending the cool air from the freezing chamber side region 68a and
the refrigerating chamber side region 68b to the freezing chamber F
and the refrigerating chamber R, respectively, and motors (not
shown) for driving the fans 72 and 74 are installed on the
circulation passages to be linked to the freezing chamber side
region 68a and the refrigerating chamber side region 68b.
Preferably, the compressor and the expansion means are formed in
the same manner as those of the first embodiment.
In the evaporator 68, a heat exchange region is divided by the
cross wall 54 so that the freezing chamber side region 68a and the
refrigerating chamber side region 68b can be disposed side by side.
As shown in FIG. 6, plurality of grooves 54a are formed on the
surface of the cross wall 54, for forming a turbulent bed to the
cool air flowing along the surface of the evaporator 68, thereby
improving heat exchange efficiency.
The evaporator 68 is a straight type thin heat exchanger in which a
plurality of cooling fins 68B are installed vertically to a
refrigerant tube 68A. As shown in FIG. 11, the freezing chamber
side region 68a and the refrigerating chamber side region 68b can
have the same area, or as depicted in FIG. 10, the freezing chamber
side region 68a can be larger than the refrigerating chamber side
region 68b. A cooling fin pitch a of the freezing chamber side
region 68a is set wider than a cooling fin pitch b of the
refrigerating chamber side region 68b, to efficiently prevent the
freezing chamber side region 68a from being frosted and improve
heat exchange efficiency in the refrigerating chamber side region
68b.
Preferably, at least one defrosting heater (not shown) is installed
at the lower portion of the evaporator 68, for performing a
defrosting operation. The defrosting heaters are also formed in the
same manner as those of the first embodiment.
The frying chamber fan 72, the refrigerating chamber fan 74, and
the motors for driving the fans 72 and 74 are formed in the same
manner as those of the first embodiment.
In accordance with the second embodiment of the present invention,
there are formed the circulation passage for the freezing chamber F
for discharging the cool air from the freezing chamber side region
68a of the evaporator 68 to the freezing chamber F, circulating the
cool air in the freezing chamber F, and re-supplying the circulated
air to the freezing chamber side region 68a of the evaporator 68,
and the circulation passage for the refrigerating chamber R for
discharging the cool air from the refrigerating chamber side region
68b of the evaporator 68 to the refrigerating chamber R,
circulating the cool air in the refrigerating chamber R, and
re-supplying the circulated air to the refrigerating chamber side
region 68b.
In the evaporator 68, the freezing chamber side region 68a is
disposed on the inner wall of the freezing chamber F, and the
refrigerating chamber side region 68b is disposed on the inner wall
of the refrigerating chamber R. Here, the freezing chamber side
region 68a and the refrigerating chamber side region 68b are
divided by the cross wall 54. Accordingly, the circulation passage
for the freezing chamber F and the circulation passage for the
refrigerating chamber R need not to be specially divided.
A connection passage 54c is formed on the cross wall 54 between the
freezing chamber F and the refrigerating chamber R, so that the
cool air can flow therethrough. A damper 54d is installed to be
opened/closed on the connection passage 54c. The damper 54d is
opened/closed by the microcomputer for controlling the operation of
the refrigerator, for supplying part of the cool air of the
freezing chamber F to the refrigerating chamber R.
FIG. 7 is a structure view illustrating a first example of a
refrigeration cycle applied to the refrigerators of FIGS. 3 and
5.
The first example of the refrigeration cycle which can be applied
to the refrigerators in accordance with the first and second
embodiments of the present invention will now be explained. The
refrigeration cycle includes a compressor 62 for compressing
refrigerants into high temperature high pressure gas refrigerants,
a condenser 64 for condensing the refrigerants compressed in the
compressor 62 into high temperature high pressure liquid
refrigerants by performing a heat exchange operation with outdoor
air, an expansion means 66 having a freezing expansion valve 66a or
a refrigerating expansion valve 66b for decompressing the
refrigerants condensed in the condenser 64 into low temperature low
pressure liquid refrigerants by controlling a decompression degree
according to a load, a three way valve 82 for controlling the
refrigerants discharged from the condenser 64 to be selectively
supplied to the freezing expansion valve 66a or the refrigerating
expansion valve 66b, and an evaporator 68 for evaporating the
refrigerants decompressed in the expansion means 66 into low
temperature low pressure gas refrigerants by performing a heat
exchange operation with air in a freezing chamber F or a
refrigerating chamber R, and generating cool air at the same
time.
The evaporator 68 is divided into a freezing chamber side region
68a and a refrigerating chamber side region 68b. A freezing chamber
fan 72 and a motor are installed to be linked to the freezing
chamber side region 68a, so that the cool air passing through the
freezing chamber side region 68a can be supplied merely to the
freezing chamber F. A refrigerating chamber fan 74 and a motor are
installed to be linked to the refrigerating chamber side region
68b, so that the cool air passing through the refrigerating chamber
side region 68b can be supplied merely to the refrigerating chamber
R.
In detail, a constant speed compressor can be used as the
compressor 62. However, the compressor 62 is preferably a capacity
variable compressor for controlling a flow rate of the refrigerants
circulated in the refrigeration cycle and controlling a compression
degree of the refrigerants. For example, an inverter compressor or
a linear compressor which can vary a rotation number is used as the
compressor 62.
The condenser 64 is a heat exchanger. In order efficiently perform
the heat exchange operation with outdoor air, a special fan (not
shown) can be installed adjacently to the condenser 64.
The freezing expansion valve 66a and the refrigerating expansion
valve 66b are disposed side by side. Refrigerant tubes formed at
the front and rear ends of the freezing expansion valve 66a and the
refrigerating expansion valve 66b are coupled to each other,
respectively. Capillary tubes having a relatively small refrigerant
tube diameter or electronic expansion valves controlling opening
can be used.
Here, the freezing expansion valve 66a and the refrigerating
expansion valve 66b are different in capacity. The freezing
expansion valve 66a has a relatively larger decompression capacity
than the refrigerating expansion valve 66b. The freezing expansion
valve 66a and the refrigerating expansion valve 66b can switch the
passages of the refrigerants according to each load.
The three way valve 82 controls the refrigerants from the condenser
64 to be supplied in one direction of the freezing expansion valve
66a or the refrigerating expansion valve 66b. Preferably, the three
way valve 82 is installed on the refrigerant tubes branched into
the freezing expansion valve 66a and the refrigerating expansion
valve 66b.
Here, the three way valve 82 controls the refrigerants to pass
through the freezing expansion valve 66a so that a temperature Tf
of the freezing chamber F can reach a set freezing temperature
Tf.sub.0, and controls the refrigerants to pass through the
refrigerating expansion valve 66b so that a temperature Tr of the
refrigerating chamber R can reach a set refrigerating temperature
Tr.sub.0.
The evaporator 68 is installed so that the freezing chamber region
66a and the refrigerating chamber side region 68b can be linked to
the freezing chamber F and the refrigerating chamber R,
respectively. The freezing chamber fan 72, the refrigerating
chamber fan 74, and the motors for driving the fans 72 and 74 are
installed on each passage.
Preferably, the evaporator 68 is a straight type thin heat
exchanger, the freezing chamber fan 72 and the refrigerating
chamber fan 74 are sirocco fans, and the motors are BLCD
motors.
While the compressor 62 is operated, the low temperature low
pressure gas refrigerants are circulated in the freezing chamber
side region 68a and the refrigerating chamber side region 68b of
the evaporator 68. Accordingly, the cool air is supplied to the
freezing chamber F or the refrigerating chamber R according to the
operations of the freezing chamber fan 72 and the refrigerating
chamber fan 74.
Here, the freezing chamber fan 72 sends the cool air from the
freezing chamber side region 68a to the freezing chamber F so that
the temperature Tf of the freezing chamber F can reach the set
freezing temperature Tf.sub.0, and the refrigerating chamber fan 74
sends the cool air from the refrigerating chamber side region 68b
to the refrigerating chamber R so that the temperature Tr of the
refrigerating chamber R can reach the set refrigerating chamber
Tr.sub.0.
The evaporator 68 is formed to individually link the freezing
chamber side region 68a and the refrigerating chamber side region
68b to the freezing chamber F and the refrigerating chamber R, and
to have circulation passages for circulating cool air in the
freezing chamber F and the refrigerating chamber R,
respectively.
The operations of the above-described components are controlled by
a microcomputer (not shown).
The operation of the first example of the refrigeration cycle will
now be described.
In a freezing mode for making the temperature Tf of the freezing
chamber F reach the set freezing temperature Tf.sub.0, the
microcomputer controls the three way valve 82 so that the
refrigerants can pass through the freezing expansion valve 66a,
operates the freezing chamber fan 72, and stops the refrigerating
chamber fan 74.
Therefore, the refrigerants are circulated through the compressor
62, the condenser 64, the freezing expansion valve 66a and the
evaporator 68. As the freezing chamber fan 72 is operated, the cool
air heat-exchanged in the freezing chamber side region 68a is
supplied merely to the freezing chamber F, to cool the freezing
chamber F.
In a refrigerating mode for making the temperature Tr of the
refrigerating chamber R reach the set refrigerating temperature
Tr.sub.0, the microcomputer controls the three way valve 82 so that
the refrigerants can pass through the refrigerating expansion valve
66b, operates the refrigerating chamber fan 74, and stops the
freezing chamber fan 74.
Accordingly, the refrigerants are circulated through the compressor
62, the condenser 64, the refrigerating expansion valve 66b and the
evaporator 68. As the refrigerating chamber fan 74 is operated, the
cool air heat-exchanged in the refrigerating chamber side region
68b is supplied merely to the refrigerating chamber R, to cool the
refrigerating chamber R.
In a freezing and refrigerating mode for making the temperature Tf
of the freezing chamber F and the temperature Tr of the
refrigerating chamber R reach the set freezing temperature Tf.sub.0
and the set refrigerating temperature Tr.sub.0, respectively, the
three way valve 82 makes the refrigerants to pass through the
freezing expansion valve 66a, the freezing chamber fan 72 is
continuously operated, and the refrigerating chamber fan 74 is
operated and stopped at intervals of a predetermined time.
As a result, the refrigerants are circulated through the compressor
62, the condenser 64, the freezing expansion valve 66a and the
evaporator 68. As the freezing chamber fan 72 is operated, the cool
air heat-exchanged in the freezing chamber side region 68a is
supplied to the freezing chamber F, and as the refrigerating
chamber fan 74 is intermittently operated, the cool air
heat-exchanged in the refrigerating chamber side region 68b is
supplied to the refrigerating chamber R during the operation,
thereby cooling both the freezing chamber F and the refrigerating
chamber R.
In a defrosting mode for making the temperature Tf of the freezing
chamber F and the temperature Tr of the refrigerating chamber R
reach a defrosting temperature Ti for removing ice from the surface
of the evaporator 68, the compressor 62 is stopped, the freezing
chamber fan 72 is stopped, and the refrigerating chamber fan 74 is
operated.
In a state where the refrigerants are not circulated, the
refrigerating chamber side region 68b of the evaporator 68 is
defrosted by the air sent by the operation of the refrigerating
chamber fan 74, and the freezing chamber side region 68a of the
evaporator 68 is defrosted by the heat transmitted from the
refrigerating chamber side region 68b.
In the defrosting mode, if the temperature Tf of the freezing
chamber F and the temperature Tr of the refrigerating chamber R do
not reach the defrosting temperature Ti, defrosting heaters
installed at the lower portion of the evaporator 68 are heated to
defrost the evaporator 68.
The first example of the refrigeration cycle improves the cooling
speed of the refrigerating chamber R more than the general
refrigeration cycle by cooling the freezing chamber F and the
refrigerating chamber R, respectively, efficiently cools a large
capacity of refrigerator, and individually effectively defrosts the
freezing chamber F and the refrigerating chamber R.
FIG. 8 is a structure view illustrating a second example of the
refrigeration cycle applied to the refrigerators of FIGS. 3 and
5.
The second example of the refrigeration cycle which can be applied
to the refrigerators in accordance with the first and second
embodiments of the present invention will now be explained. The
second example of the refrigeration cycle is basically identical to
the first example of the refrigeration cycle. However, a connection
passage (not shown) is formed between the freezing chamber F and
the refrigerating chamber R, so that the cool air can flow
therethrough, and a damper 76 is installed to be opened/closed on
the connection passage.
Accordingly, the second example of the refrigeration cycle is
operated in the same manner as the first example of the
refrigeration cycle. However, in the freezing mode, if the
temperature Tr of the refrigerating chamber R is higher than the
set refrigerating temperature Tr.sub.0, the damper 76 is opened to
supply part of the cool air of the freezing chamber F to the
refrigerating chamber R, thereby controlling the temperature Tr of
the refrigerating chamber R.
That is, when the temperature Tr of the refrigerating chamber R
increases in the freezing mode, the temperature Tr of the
refrigerating chamber R can be easily controlled by supplying the
cool air of the freezing chamber F having a relatively low
temperature to the refrigerating chamber R. Therefore, the
refrigerating chamber fan 74 needs not to be driven, which results
in low power consumption.
FIG. 9 is a structure view illustrating a third example of the
refrigeration cycle applied to the refrigerators of FIGS. 3 and
5.
The third example of the refrigeration cycle which can be applied
to the refrigerators in accordance with the first and second
embodiments of the present invention will now be explained. The
refrigeration cycle includes a compressor 62 for compressing
refrigerants into high temperature high pressure gas refrigerants,
a condenser 64 for condensing the refrigerants compressed in the
compressor 62 into high temperature high pressure liquid
refrigerants by performing a heat exchange operation with outdoor
air, an expansion means 66 having a freezing expansion valve 66a or
a refrigerating expansion valve 66b for decompressing the
refrigerants condensed in the condenser 64 into low temperature low
pressure liquid refrigerants by controlling a decompression degree
according to a load, first and second solenoid valves 84a and 84b
installed on refrigerant tubes formed at the front ends of the
freezing expansion valve 66a and the refrigerating expansion valve
66b, respectively, for controlling the refrigerant tubes to be
opened/closed, and an evaporator 68 for evaporating the
refrigerants decompressed in the expansion means 66 into low
temperature low pressure gas refrigerants by performing a heat
exchange operation with air in a freezing chamber F or a
refrigerating chamber R, and generating cool air at the same
time.
The evaporator 68 is divided into a freezing chamber side region
68a and a refrigerating chamber side region 68b. A freezing chamber
fan 72 and a motor are installed to be linked to the freezing
chamber side region 68a, so that the cool air passing through the
freezing chamber side region 68a can be supplied merely to the
freezing chamber F. A refrigerating chamber fan 74 and a motor are
installed to be linked to the refrigerating chamber side region
68b, so that the cool air passing through the refrigerating chamber
side region 68b can be supplied merely to the refrigerating chamber
R.
In detail, the compressor 62, the condenser 64, the freezing
expansion valve 66a, the refrigerating expansion valve 66b, the
evaporator 68, the freezing chamber fan 72 and the refrigerating
chamber fan 74 are formed in the same manner as those of the first
embodiment.
The expansion means 66 further includes an auxiliary expansion
valve 66c for intermediately cooling the refrigerants from the
evaporator 68 by decompression, and resupplying the refrigerants to
the compressor 62. That is, the refrigerants are intermediately
cooled between the evaporator 68 and the compressor 62, thereby
improving efficiency of the whole refrigeration cycle.
The first and second solenoid valves 84a and 84b are installed on
the refrigerant tubes at the front ends of the freezing expansion
valve 66a and the refrigerating expansion valve 66b, for
controlling the refrigerant tubes to be opened/closed. Therefore,
the first and second solenoid valves 84a and 84b supply the
refrigerants from the condenser 64 to the freezing expansion valve
66a, the refrigerating expansion valve 66b, or both the freezing
expansion valve 66a and the refrigerating expansion valve 66b.
The operations of the above-described components are controlled by
a microcomputer (not shown).
The operation of the third example of the refrigeration cycle will
now be described.
In a freezing mode for making a temperature Tf of the freezing
chamber F reach a set freezing temperature Tf.sub.0, the
microcomputer opens the first solenoid valve 84a and closes the
second solenoid valve 84b, so that the refrigerants can pass
through the freezing expansion valve 66a, operates the freezing
chamber fan 72, and stops the refrigerating chamber fan 74.
Therefore, the refrigerants are circulated through the compressor
62, the condenser 64, the freezing expansion valve 66a, the
evaporator 68 and the auxiliary expansion valve 66c. As the freeing
chamber fan 72 is operated, the cool air heat-exchanged in the
freezing chamber side region 68a is supplied merely to the freezing
chamber F, to cool the freezing chamber F.
In a refrigerating mode for making a temperature Tr of the
refrigerating chamber R reach a set refrigerating temperature
Tr.sub.0, the microcomputer closes the first solenoid valve 84a and
opens the second solenoid valve 84b, so that the refrigerants can
pass through the refrigerating expansion valve 66b, operates the
refrigerating chamber fan 74, and stops the freezing chamber fan
72.
Accordingly, the refrigerants are circulated through the compressor
62, the condenser 64, the refrigerating expansion valve 66b, the
evaporator 68 and the auxiliary expansion valve 66c. As the
refrigerating chamber fan 74 is operated, the cool air
heat-exchanged in the refrigerating chamber side region 68b is
supplied merely to the refrigerating chamber R, to cool the
refrigerating chamber R.
In a freezing and refrigerating mode for making the temperature Tf
of the freezing chamber F and the temperature Tr of the
refrigerating chamber R reach the set freezing temperature Tf.sub.0
and the set refrigerating temperature Tr.sub.0, respectively, the
first solenoid valve 84a is opened and the second solenoid valve
84b is closed, so that the refrigerants can pass through the
freezing expansion valve 66a, the freezing chamber fan 72 is
continuously operated, and the refrigerating chamber fan 74 is
operated and stopped at intervals of a predetermined time.
As a result, the refrigerants are circulated through the compressor
62, the condenser 64, the freezing expansion valve 66a, the
evaporator 68 and the auxiliary expansion valve 66c. As the
freezing chamber fan 72 is operated, the cool air heat-exchanged in
the freezing chamber side region 68a is supplied to the freezing
chamber F, and as the refrigerating chamber fan 74 is
intermittently operated, the cool air heat-exchanged in the
refrigerating chamber side region 68b is supplied to the
refrigerating chamber R during the operation, thereby cooling both
the freezing chamber F and the refrigerating chamber R.
In a defrosting mode for making the temperature Tf of the freezing
chamber F and the temperature Tr of the refrigerating chamber R
reach a defrosting temperature Ti for removing ice from the surface
of the evaporator 68, the compressor 62 is stopped, the first and
second solenoid valves 84a and 84b are closed, the freezing chamber
fan 72 is stopped, and the refrigerating chamber fan 74 is
operated.
In a state where the refrigerants are not circulated, the
refrigerating chamber side region 68b of the evaporator 68 is
defrosted by the air sent by the operation of the refrigerating
chamber fan 74, and the freezing chamber side region 68a of the
evaporator 68 is defrosted by the heat transmitted from the
refrigerating chamber side region 68b.
In the defrosting mode, if the temperature Tf of the freezing
chamber F and the temperature Tr of the refrigerating chamber R do
not reach the defrosting temperature Ti, the first and second
solenoid valves 84a and 84b are opened to circulate the
refrigerants having a relatively high temperature along the
evaporator 68, and defrosting heaters installed at the lower
portion of the evaporator 68 are heated to defrost the evaporator
68.
Identically to the first example of the refrigeration cycle, the
third example of the refrigeration cycle improves the cooling speed
of the refrigerating chamber R more than the general refrigeration
cycle by cooling the freezing chamber F and the refrigerating
chamber R, respectively, efficiently cools a large capacity of
refrigerator, and individually effectively defrosts the freezing
chamber F and the refrigerating chamber R.
FIG. 12 is a flowchart showing sequential steps of a method for
controlling an operation of a refrigerator in accordance with a
preferred embodiment of the present invention.
The method for controlling the operation of the refrigerator will
now be explained with reference to FIG. 12, and the components of
the refrigerator will now be explained with reference to FIGS. 7 to
9.
In the first step, a temperature Tf of a freezing chamber F and a
temperature Tr of a refrigerating chamber R are compared with a set
freezing temperature Tf.sub.0 and a set refrigerating temperature
Tr.sub.0, for sensing a freezing load and a refrigerating load, and
an operation mode of the refrigerator is determined (refer to S1,
S2, S3, S5, S7 and S8).
In detail, the set freezing temperature Tf.sub.0 and the set
refrigerating temperature Tr.sub.0 are set by the user or
automatically set, and the temperature Tf of the freezing chamber F
and the temperature Tr of the refrigerating chamber R sensed in the
freezing chamber F and the refrigerating chamber R are compared
with the set freezing temperature Tf.sub.0 and the set
refrigerating temperature Tr.sub.0, thereby determining the
operation mode of the refrigerator.
Here, when the temperature Tf of the freezing chamber F is higher
than the set freezing temperature Tf.sub.0 and the temperature Tr
of the refrigerating chamber R is higher than the set refrigerating
temperature Tr.sub.0, a freezing and refrigerating mode is
selected, when the temperature Tf of the freezing chamber F is
higher than the set freezing temperature Tf.sub.0 but the
temperature Tr of the refrigerating chamber R is lower than the set
refrigerating temperature Tr.sub.0, a freezing mode is selected,
when the temperature Tf of the freezing chamber F is lower than the
set freezing temperature Tf.sub.0 but the temperature Tr of the
refrigerating chamber R is higher than the set refrigerating
temperature Tr.sub.0, a refrigerating mode is selected, and when
the temperature Tf of the freezing chamber F is lower than the set
freezing temperature Tf.sub.0 and the temperature Tr of the
refrigerating chamber R is lower than the set refrigerating
temperature Tr.sub.0, a cooling mode is not selected.
In the second step, a cooling operation is performed by sending
cool air to the freezing chamber F and the refrigerating chamber R,
the freezing chamber F or the refrigerating chamber R according to
the mode set in the first step (refer to S4, S6 and S9).
Here, when the freezing and refrigerating mode is selected, a
compression flow rate and a decompression degree are maximized, and
the cool air is sent to the freezing chamber F and the
refrigerating chamber R.
Therefore, refrigerants are compressed, condensed, expanded and
evaporated sequentially through the compressor 62, the condenser
64, the expansion means 66 and the evaporator 68, for cooling air
near the evaporator 68. Here, the ambient air can be rapidly cooled
by remarkably controlling the compression flow rate and the
decompression degree. When a freezing chamber fan 72 and a
refrigerating chamber fan 74 installed at the upper portions of a
freezing chamber side region 68a and a refrigerating chamber side
region 68b of the evaporator 68 are operated, the cool air passing
through the freezing chamber side region 68a of the evaporator 68
is circulated in the freezing chamber F, and the cool air passing
through the refrigerating chamber side region 68b of the evaporator
68 is circulated in the refrigerating chamber R.
When the freezing mode is selected, the compression flow rate and
the decompression degree are relatively remarkably controlled, and
the cool air is sent merely to the freezing chamber F.
Only the freezing chamber fan 72 is operated, and thus the cool air
passing through the freezing chamber side region 68a of the
evaporator 68 is circulated in the freezing chamber F.
In the freezing mode, if the temperature Tr of the refrigerating
chamber R gets higher than the set refrigerating temperature
Tr.sub.0, part of the cool air of the freezing chamber F can be
supplied to the refrigerating chamber R.
When the refrigerating mode is selected, the compression flow rate
and the decompression degree are relatively slightly controlled,
and the cool air is sent merely to the refrigerating chamber R.
Only the refrigerating chamber fan 74 is operated, and thus the
cool air passing through the refrigerating chamber side region 68b
of the evaporator 68 is circulated in the refrigerating chamber
R.
Especially, in the refrigerating mode, a temperature of the
evaporator 68 is preferably higher than that of the freezing
chamber F and lower than that of the refrigerating chamber R.
In the third step, while the cooling operation is performed in each
mode in the second step, the temperature Tf of the freezing chamber
F and the temperature Tr of the refrigerating chamber R are
compared with a previously-inputted defrosting temperature Ti, and
a defrosting mode is determined according to the comparison result
(refer to S10 and S11).
Here, the surface of the evaporator 68 may be frosted during the
cooling operation in each mode. The frosted surface of the
evaporator 68 reduces heat exchange efficiency of the evaporator
68. Accordingly, the surface of the evaporator 68 needs to be
defrosted.
Because the evaporator 68 does not perform a heat exchange
operation with ambient air due to frost, the temperature Tf of the
freezing chamber F or the temperature Tr of the refrigerating
chamber R relatively increases. If the temperature Tf of the
freezing chamber F or the temperature Tr of the refrigerating
chamber R gets higher than the defrosting temperature Ti, the
defrosting mode is started.
In detail, in the defrosting mode, in a state where the
refrigerants are stopped not to flow, the refrigerating chamber fan
74 is operated so that the air of the refrigerating chamber R
having a relatively high temperature can be sent and circulated to
defrost the refrigerating chamber side region 68b of the evaporator
68. Here, the freezing chamber side region 68a of the evaporator 68
is also defrosted by heat transfer effects.
In addition, in the defrosting mode, the high temperature high
pressure liquid refrigerants are supplied to the evaporator 68, and
the refrigerating chamber fan 74 is rotatably operated, thereby
efficiently performing the defrosting operation.
Furthermore, in the defrosting mode, defrosting heaters installed
at the lower portion of the evaporator 68 are heated to rapidly
perform the defrosting operation.
As discussed earlier, the side-by-side type refrigerator where the
freezing chamber F and the refrigerating chamber R are disposed
side by side in accordance with the preferred embodiments of the
present invention has been described with reference to the
accompanying drawings. However, it is understood that the present
invention should not be limited to these preferred embodiments but
various changes and modifications can be made by one skilled in the
art within the spirit and scope of the present invention as
hereinafter claimed.
* * * * *